Two-speed and reversing turbine



PATENTED FEB. 16,1904.

J. WILKINSON. TWO SPEED AND REVERSING TURBINE.

:APPLIUATION FILED D30. 16, 1903.

4 SHEETS-8HEET K0 MODEL.

; PATENTED FEBQ16, 1904.

J. WILKINSON; TWO SPEED AND REVER$ING TURBINE.

APPLICATION FILED 111:0. 1B. 1903.

' 4 SHEETS-SHEET 2.

H0 MODEL.

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w 36 hf W a MW m n/if/zesses No. 752,496. H PATENTBDVPERIIG, 1904.

J. WILKINSON. TWO SPEED AND REVERSING TURBINE. AI PLIUATION FILED DEC. 16, 1903.

V .4 SHEETS-SHEET 4..

N0 MODEL.

3i r-wento'a UNITED STATES 1 Patented February 16, 1904.

PATENT OFFICE.

JAMES WILKINSON, OF BIRMINGHAM, ALABAMA, ASSIGNOR TO WILKINSON STEAM TURBINE COMPANY, A CORPORATION ALABAMA.

TWO-SPEED AND RE VERSING TURBINE.

SPECIFICATION forming part of Letters Patent No. 752,496, dated February 16, 1904.

' Application filed December 16,1903. Serial No. 185,416. (No model.)

. To all whom it may concern:

Be it known that I, J AMES WILKINSON, a citi-' zen of the United States, residingat Birming-' ham, in the county of Jefferson and State Ofi Alabama, have invented new and useful Irnprovements in Two-Speed and Reversing Turbines, of which the following is aspecification.

My invention relates to improvements in elastic-fluid turbines, more particularly adapt.

ed for marine propulsion and designed to operate at full and cruising speeds and to act as a reversing-engine. I

It is the object of my present invention to construct a turbine capable of these several driving effects and to provide a governing mechanism for controlling and regulating the turbine so that it will operate at the highest effici'ency at all times.

With these objectsin view I provide the tur-Q bine, which may be of any desired type, but preferably one in which the velocity of the fluid is fractionally abstracted, with a plurality of concentric rows of working passages at different radial distances from the shaft center, each row being designed to rotate the bucket-wheels I at a determined rate of speed or in a given dlrection.

sages are actuated by a fluid-pressure-governing mechanism which is an adaptation and improvement on the serial valve controlling mechanism shown and described in a pending application.

My invention comprises the details of constru ction and arrangement of parts hereinafter described, and more particularly pointed out in the claims, reference being had to the accompanying drawings, illustrating my inven to the control of rotary valves 7, 8, and 9,

verse section through the line a m, Fig. 2,

Valves controlling the supply and flow of motor fluid through said working pas-,

showing the governor-cylinder in communication with'the controller-fluid conduits. A set of three pipes are also shown leading each to a valve-motor for three working passages disposed in radial alinement at different distances from the shaft. Figs. 5 and 6 show the compound valve indifferent operating positions calculated to divert the governed actuating pressure to one or the other row of working passages; and Fig. 7, is a detail view, broken away, of said valve. Fig. 8 is an enlarged sectional view of a set of admissionvalves and actuating-motors therefor. 9 is 'a section along the line a; as of Fig.8,

showing the dilferential piston in elevation.

.11 is a detail viewof a dowel-pin used to se- Fig. 12 is curethe valve-crank in position. a sectional View through. the shouldered periphery of a diaphragm, showinga set of stagevalves and a compound rotor-wheel. Figs.

13, 14, and 15 are views through lines at m, a m, and :r m of Fig. 12. Figs. 16 and '17 are side and end views of a single-ported stage or supply valve, and. Fig. 18 is a detail view of the crank of said valve.

. Similar reference-numerals refer to the same parts throughout the drawings.

As illustrated, my invention is applied to a multiple-stage elastic fluid turbine in which the velocity of the fluid-pressure is fractionally abstracted. A port 1, communicating with a suitable source of pressure, opens into an annular supply-passage 2, formed in the head 3 of the turbine, from which pressure enters one or the other of three concentric rows of nozzle-passages 4, 5, and .6, subject seated three in each radially-disposed valveseat bored into the periphery of said head. The interior of the turbine is divided into stages or wheel-compartments by transverse diaphragms 10, which are enlarged or shouldered around their peripheries to enable the stage-valves 7*, 8*, and 9 and their operating mechanism to be seated therein and control the flow through nozzle-passages 4, 5, and 6 between the several compartments. The

Fig.

. ment across the rows.

- to prevent leakage.

head 3 and diaphragms are peripherallyflanged to form the side walls of these compartments and constitute, in combination with the exhaust-head 11, the inner casing of the turbine. To strengthen the turbine and secure its parts firmly in position, I surround the inresponding female threads formed in saidshell at the other end from shoulder 13, so that between these parts the turbine-sections are securely held in place. The exhaust or condenser head 11 preferably forms a continuation of the inner casing and has a port 15 leading downwardly between the standards '16, to which the shell is securely bolted. This head also carries a bearing 17 for one end of a turbine-shaft 18, which is suitably packed One or more propellers 19 are driven by shaft 18, which is supported by an intermediate bearing 20. Within the turbine and rigidly secured to this shaft are a plurality of rotor-wheels 21, one of which is disposed within each compartment and provided with three concentric circumferential rows of buckets 22, 23, and 24, arranged to receive the discharge of motor fluid from nozzles 4, 5, and 6, respectively. The several succeeding nozzle-passages and intermediate rows of revolving buckets form circumferential rows of concentric working passages, which I shall refer to as 4, 5, and 6. Each row has the same number of nozzles, which are preferably disposed in radial aline- In this manner one circular valve-opening forms a seat for three valves 7, 8, and 9 or 7 8, and 9. To simplify construction, it is also desirable to dispose the supply-passage 2 within the inner rowof nozzles 6 and bore or otherwise provide branch passages 25, leading from passage 2 and admitting pressure to radial rows of nozzles 4, 5, and 6. These branch passages and the valve-openings preferably lead from the periphery of head 3 inwardly, their outer ends being closed by screw-plugs 26 and 27,

respectively, Fig. 8.

The working passages 6 are disposed and proportioned to drive the turbine at a less power and in a reverse direction to that of passages 5, which are designed for afull-speedahead drive. The outer row of passages 4 are for use when it is desired to propel the vessel at half or cruising speed, which driving effect is obtained without loss of economy by providing each wheel with two parallelrows of buckets 22 and mounting stationary intermediates or guides 28 in depending flanges 29 of head 3 and diaphragmslO. The speed of rotation of the turbine varies directly with the number of rows of buckets, 'each of which fractionally abstracts the velocity .of the motor fluid. Hence by doubling the number of rows the speed is reduced by one-half, while the turbine acts always at the highest economy. The driving effect of the several rows of working passages may be varied at will or interchanged; but it will be obvious that but one of said rows must be driving the turbine ata time. This will be controlled by moving the valves in the working passages to be made inactive to a closed position, while the valves in the active passage will be opened or closed, subject to the action of my improved governing mechanism hereinafter described.

I provide fluid-pressure motors 30, 31, and 32 for operating the supply-valves 7, 8, and 9, respectively, said motors comprising compound cylinders 33 and 34, formed as chambers bored into the head 3 and closed pressure-tight by screw-plugs 35. Differential pistons 36, having high and low pressure heads 37 and 38, respectively, reciprocate in said cylinders and are connected by links 39 to cranks 40 of valves 8 and cranks 41 of valves 7 and 9. It is desirable on account of the length of valves 8 to operate them by cranks disposed near their centers. I therefore leave a partition 42 in the nozzles of the working passages 5, which subdivide each nozzle into two passages, and I provide the valves 8 and 8 with two ports, one of which is disposed in alinement with and acts to control the admission of fluid to each passage. The cranks 40, by which these valves are operated, enterv an opening 43 between the ports :and :opposite to the partition 42, which is formed with a recess 44, leading downwardly from cylinder 34. The cranks are disposed and move in this recess, being pivotally connected at 45 to the links 39, which in turn are pivotally connected to the heads 38 at 46. I secure the cranks in position in the valves 8 by dowel-pins. 47, having threaded heads 48, Fig. 11, which are inserted in longitudinal openings passing partly through the valve and on either side of a port. These openings are countersunk and threaded at theirouter ends, so' that when the crank 40 is in position the holes 49 therein are in r alinement with said pin-openings, and the inner ends of the dowel-pins will pass through said hole 49 and firmly secure said crank in position. The cranks 41, used to rotate valves 7 and 9, are connected to their ends and have '4, 5, and 6 into their respective cylinders 34 to admit the full pressure of the motor fluid beneath heads 38 of the pistons 36. Passages 54 lead upwardly through the head 3 from the first wheel-compartment and enter the cylinders 33 to admit beneath the heads 37 the pressure of the first stage. Passages 55, 56, and 57 lead, respectively, through the plugs 35 and admit a governed pressure above the piston 36. When. this governed pressure is sustages.

perior to the combined effect of the supply and stage pressure beneath it, piston 36 will move downwardly and the supply-valves'will close, and vice versa, when the pressure below is superior the valves will be moved to their open position, as shown in Fig. 9. If the turbine be of the one-stage type, the mechanism described will act under the control of a governing mechanism to regulate the supply of the motor fluid according to the load. If, however, as is preferable, the turbine be of the multiple-stage type, I lead from each of the passages 55, 56, and 57 branch passages 55, 56", and 57* through the head to its periphery and downwardly through the casing, each passage 55 leading to a row of motors actuating the stage-valves 7 across the several stages, and passages 56 and 57 a lead in a similar manner to rows of motors controlling valves 8 and 9, respectively, across the The stage-actuating motors comprise single cylinders 58, formed in the shoulders of the diaphragm in the same manner as chambers 33 and 34 in the head, and are closed-by plugs 59. Pistons 6O reciprocate in these cylinders and are connected by pivoted links 39 to cranks 41, which actuate the stage-valves.

Passages 53 admit the preceding stagepres-.

sure below piston 60, while the governed pressure is admitted above said piston through passages 55, 56, and 57 When the governed pressure in any one of the passages 55, 56, or 57 rises sufiiciently to close the supplyvalves controlled thereby, it will act through these passages 55, 56 or 57 a to close a cor responding row of stage-valves across the several stages, so that when all of a row of supply-valves are closed the stage-valves throughout the working passages controlled by said supply-valves will also be closed, and in this manner two of the rows of working passages can be closed and maintained inactive; thisit follows that the governing mechanism controlling the supply-valves in the active working passages will simultaneously control the stage-valves in said passages.

The governing mechanism comprises a controller-valve casing 61 and a governed-fluidpressure cylinder 62, preferably formed integral therewith. This cylinder is open to an exhaust or condenser pressure through a passage 63, which leads by pipeto the atmosphere or to the exhaust-head 11..v High or escaping directly through passage 63 by a boiler pressure is admitted to cylinder 62 through passage 64 and is prevented from governor-shifted throttling-piston 65, formed .with a wedge-shaped recess 66 and a groove 67 leadingaround the piston near one end and an oppositely and reversely disposed similarly-shaped recess 68 and groove 69 near the other end. The portions of the piston not cut away fit pressure-tight within the cyl- 'inder, and in this manner communication between the recesses and between them and the From gear 75, driven through suitable speedreduc-' ing mechanism from the turbine-shaft 18. This gearing is preferably mounted on the supply end bearing 7 6 of the turbine. The shaft 73, which need only be squared throughout that portidh which passes through the'piston and its stems for the purpose of ro-' tating them, has mounted on its upper end a centrifugal governor 7 7 within whose casing are pivotally mounted two levers 78, weighted at their upper ends and adapted at their inner ends to engage a circular collar 79. By this means as the speed of rotation of shaft 7 3 varies the governor will raise or lower-the rotating piston 65, which is so constructed that as it moves downwardly to expose the pressure inlet-port it throttles the exhaust port,'and vice versa, as it moves upwardly the inlet-port is throttled as the exhaust is exposed. This throttling actionof the piston creates within the recess 68, which is in continuous communication with the fluid-pressure entering the cylinder throughpassage 64 except at one extreme of its travel, a variable governed pressure, whose potential is controlled by the position of the piston relative-to the pressure-inlet. Between the passages 63' and 64 a third passage leads fromthe cylinder 62 to the upper central portion of the valve-casing 61. Within this casing in chambers suitably .provided therefor 1 arrange two rows of serially-connected controller-valves A to F and A to F, actuated-by fluid-pressure and operating in the manner described in a'pending application filed by me, in which was disclosed a series of compound cylinders connected-up so that a governed variable fluid-pressure and a constant pressure were delivered to opposite end cylinders of the series and conducted serially theretoo through until they opposed each other in the cylinder representing the critical point of regulation. It being understood that each cylinder controls one or more valves and has a compound piston-valve therein whose differential varies from that of the other pistons and which as it moves serves as a valve to control the flow of fluid to the adjacent cylinders of the series, it follows that as thepotential of the variable fluid-pressure increases or falls more-or less of the pistons will move successively against the constant pressure to open or close turbine valves. .As shown in Figs. 2 and 4, each valve comprises low and high pressure cylinders81 and 82, Within which a differential piston having low and high pressure heads 83 and 84 moves. Y Branchpassages a passage 86 or 88 to the exhaust. portions of the cylinders and pistons of the 85 conduct the governed fluid-pressure form passage 80 and deliver it to the end of cylinders 81 and 81. Considering all the pistons lowered, this fluid will pass serially from cylinder to cylinder by passages 86, leading from the side of each cylinder to the top of the succeeding cylinder. Passages 87 conduct the high constant pressure in passage 64 to the ends of cylinders 82 and 82*, from which if the pistons be all raised it will pass through the series of cylinders 82 to valves A and A. Passages 88 lead from the side of each cylinder to the bottom of the succeeding cylinder. Cylinders 81 are open to exhaust pressure through passages 89, leading from the lower ends of cylinders 81 to a common passage 90, passing longitudinally through casing 61. By this means and suitable ports between cylinders 81 and 82 exhaust-pressure exists between'the piston-heads, which as they move to their upper or lower positions open The prosucceeding valves in a series vary, so that a governed pressure of increasing potential will move the pistons down successively against the pressure in cylinders 82, and it will be noted that when a valve, as C, Fig. 2, is up it cuts off the governed pressure from the succeeding cylinders 81 to 81 and similarly when the piston is down, as B, Fig. 2, the high pressure is stopped at that cylinder. As the piston C moved up it opened passage 86, leading to the valve D, to the exhaustpressure, thus releasing all pressure from above piston D, causing it to be locked open by the pressure in cylinder 82 In the same 1 manner as piston B moved down it cut off the constant pressure from passage 88, leading to cylinder 82*, and opened it to the exhaust and at the same time admitted governed pressure to passage 86, leading to cylinder 82. A given potential of the governed power will hold a given number of valves down; also, a given mean potential of a pulsatory supply of governed fluid-pressure will pulsate a given valve. This pulsatory supply of governed fluid-pressure is effected by the alternate opening of the passage 80 to the high and exhaust pressure in recesses 68 and 66. The controller-valves move sensitive to speed variations by reason of the fact that the governor is afiected thereby and moves its piston to throttle the ports 63 and 64 and vary the potential of the power in recess 68 and the rapidity of the exhaust through recess 66 and passage 63, so that a varying mean potential of the governed pressure is obtained. In utilizing the action of these valves to control the turbine-valves I lead passages 91 from each passage 88 and from the sides of the end cylinders 82 and 82 of the two series to a rotary valve 92, seated in a longitudinal circular seat bored through the casing and provided with a crank 93, by which it may be rotated to one of its three operating positions.

(Illustrated in Figs.4, 5, and 6.) Opposite each passage 91 and in the same transverse plane therewith'in said valve-seat are three ports leading to passages 55, 56, and 57, which enter cylinders 33 of a radial row of valves 7, 8, and 9. The compound valve 92 controls all the sets of passages 55, 56, and 57 around the turbine, being provided with a transverse passage 94, leading from a curved recess95 opposite each passage 91. This recess 95 is sufficiently wide to maintain 91 in communication with 94 in all of its three operating positions-41. e. when in alinement with one or the other of passages 55, 56, and 57. Rings of packing around valve 92 prevent leakage of pressure between the ports leading to each set of passages. From the passage 87 a series of short by-passes 97 conduct the high pressure to two of each set of passages 55, 56, and 57 by opening into a recess 98, communicating with a similar recess 99011 the other side of port 94 by passage 100, leading around said. port, as shown in dotted lines, Fig. 7. Recesses 98 and 99 being always supplied with pressure cause it to enter passages 56 and 57 Fig. 4, passages 55 and 57, Fig. 5, and passages 55 and 56, Fig. 6, and being admitted to the supply and stage valve actuating motors moves their position down against the pressure below them and closes the supply-valves. In this manner two rows of working passages are maintained inactive, while the turbine is driven by the motor fluid admitted. to the remaining row of active passages.

To illustrate the action of the governor control of the active passages, I will refer to Figs; 3 and 4, in which passage 94 is shown open to passages 55, which lead to the motors 30, controlling valves 7 and 7 a in working passages 4. Before the turbine is started a coiled spring 101, disposed around the upper end of shaft 73 and seated against a collar 102 thereon, engages an extension 103 of stem 70 and forces the latter down against the action of the governorlevers 78 upon collar 79. This opens passage 64 fully and closes exhaust-passage 63, so that if recess 68 be moved into communication with passage the full high pressure will move all the controllervalves down and cut of? high pressure from all passages 91 and 55, so that the pressure below the motors pistons raises them to open the valves in the outer row of working passages. The admission of motor fluid to passage 2 will cause the turbine to rotate, and the governor, sensitive to the increasing speed, will raise piston 65 to reduce the potential of the governed power delivered to passage 80 until in cylinder F it falls below that of the constant pressure, when the piston will move up and the high pressure will pass .through 88 to cylinder E and through passages 91, 94, and'55 to one or more motors 30 to close valves 71 and reduce the supply of motor fluid. Each of the passages 55, 56, and 57 may lead to any desired number of motors IIO in their respective rows. As the load con tinues to increase the pistons in the cylinders E, I), C, &c., successively rise and the high pressure closes more valves 7 until at the-ex treme of the movement of piston pressure from passage 65 is entirely out oii and all the controller-valves are up, so that all of the turbine-valves 7 are closed. The action is reversed as the speed decreases.

Since the speed of rotation of the turbine when driven by passages 1 will be only half of its normal speed, it is necessary to make provision for the eflect of this change of speed on the governor to enable it to exert the same control over the fluid-supply under different speeds. I provide the governor-casing 77 with a threaded cylindrical top portion 10 1 and screw thereon a cap 105. This cap is hollow and has disposed within it and around spring 101 a second coiled spring 106, which also engages extension 103 and acts to increase the resistance to the governors action in shifting piston 65. Both springs are used for the full-speed operation of the turbine; but when the vessel is under half or cruising speed cap 105 will be unscrewed until spring 106 exerts no influence against stem 70, and the governor will then act sensitive to a lower speed of rotation. To reduce friction between collar 7 9 and lever 7 8, I provide the latter with a roller 107, pivotally mounted at its end.

By moving valve 92 to the position shown in Fig. 5 and screwing cap to position shown in Fig. 3 the turbine will drive the vessel forward at full speed, and by moving it to position shown in Fig. 6 the vessel will be reversed at full speed.

To enable the turbine to be controlled by hand in'caseof injury to the governor and also to assist in starting it when passage was open to exhaust and all the turbine-valves closed, I provide each controller-valve with a stem 108, leading through the top of the easing 62. Stuffing-glands 109 prevent the leakage of pressure from the cylinders. Theaction of the controller-valves may be readily followed by watching the movement of these stems. As shown in Fig. 2, the valves A, A, B, and B are down and the rest up. The con troller-valves may be successively moved down by hand and locked in that position in any suitable manner to control the turbine, and if all the, turbine-valves are closed and pressure exist in supply-passage 2 by moving valve A down a turbine-valve will be opened and admitting pressure to the engine will cause the rotation of the piston 65, which will admit high governed pressure to the series of cylinders to open all the valves.

The governor-casing 7 7 is keyed to the shaft 73 by pin 110, and I provide cap with a handle 111 for unscrewing it.

It may here be noted that the corresponding valves of both series may be designed to move simultaneously or alternately in succession, or, if desired, they may all be arranged in a single series, when the governed pressure will be led to one end of the casing and the high pressure to the other.

I provide the inner circumferential walls of the wheelchambe'rs with annular ribs 113, extending substantially at right angles from the compartment Wall and provided with upturned edges to form receptacles for the water of condensation thrown ofi by the rotation of the wheel 21. Any desired number of these ribs may be used, and they may be formed integral with the casing or mounted on separate rings 114:, which will also serve the purpose of locking the stationary intermediates 2-8 in position. Instead of 'endeavoring to withdraw this water of condensation from these receptacles I intend to revaporate it by providing a passage 115, leading around the compartment-casing and acting to superheat the rib projections 113, so that they will act to evaporate the water held on them. Steam or any other heating medium may be circulated through the passage 115 by inlet and outlet passages 116 and 117, and the passage 115 may be formed in any desired manner, but preferably by a grooved recess 'and an annular grooved filler-strip 118, through which the passages 116 and 117 may lead. It will be noted that the intermediates 28 will be also superheated by this means and that their baseblocks will-act in the same manner as ribs 113 to evaporate the condensation collected thereon.

Having thus described my invention, whatI claim as new, and desire to secure by Letters Patent, is

1. In a motor, a plurality of valves controlling the supply offluid to induction-passages, and a plurality of governed fluidactuated valves controlling the operation of said supply-valves.

2. In a motor, a plurality of motor-fluidsupply valves, nozzle-passages, and governorcontrolled fluid-actuated means controlling actuating means for said motor-fluid valves.

3. In a motor, a plurality of motor-fluid valves, and a controlling mechanism comprising a casing, fluid-actuated controller-valves therein controlling means to actuate said motor-fluid valves, and means to control the action of said controller-valves.

1. In a motor, aplurality of fluid-actuated controller-valves arranged in. a casing, a plurality of motor-fluid valves and means controlled by said controller-valves to actuate said motor-fluid valves.

5; In a motor, a valve-casing, a plurality of valves therein, means to serially transmit a governed power from valve to valve to operate them successively, and means controlled by said valves to operate motor-fluid valves.

6. In a motor, a plurality of motor-fluid valves, a controller power means, a plurality of devices adapted to be independently actuated by variations in the potential of said means to deliver a varying actuating power to valves the operation of which is controlled by ing a casing, a plurality of controller-valves power means comprising a casing, a plurality a plurality of fluid-actuated controller-valves,

power means, and means controlled by said devices to actuate said motor-fluid valves.

7. In a motor, a plurality of motor -fluid valves, anda governing mechanism compris ing a plurality of controller devices, means to serially transmit an actuating power from one to another of said devices, and means under the control of said devices to actuate said motor-fluid valves.

8. In a motor, a plurality of motor-fluid valves, a plurality of controller-valves, fluidpressure means to serially actuate-said controller-valves, and fluid-pressure motors to actuate said motor-fluid valves controlled by said controller-valves.

9. In a governing mechanism for motors, a casing provided with a plurality of fluid-actuated controller-valves, a governing means to control the action of said valves, and motorfluid valves which operate under the control of said controller-valves.

10. In a motor, a plurality of motor-fluid valves and a governing mechanism comprising a casing, a series of valve-cylinders therein, passages leadingfrom cylinder to cylinder, means to create and deliver a fluid-pressure of varying potential successively to said cylinders, valves in said cylinders, and means under the control of said valves to actuate said motor-fluid valves.

11. In a motor, a plurality of motor-fluid valves and a governing mechanism compristher'ein, means to serially transmit an actuating power to said valves, and means controlledby said valves to actuate said motor fluid valves. 3

12. In a governing mechanism for motors, a plurality of fluid-actuated controller-valves, fluid-conducting passages leading from valve to valve which are successively opened to an actuating fluid by the movement of the valves from which they lead, and means controlled: by said valves to actuate motor-fluid valves.

13. In a governing mechanism for motors, a plurality of motor-fluid valves, a controller.

of independently-actuated devices serially coupled up and adapted each to control the oper- .ation of one of agroup of independent motorfluid valves.

14. In a governing mechanism for motors, a plurality of valves coupled up 1n series,

avarying number of said valves, means to vary the actuating power, and motor-fluid.

said first-mentioned valves.

15. In a governing mechanism tor motors,

fluid-conducting passages leading fromvalve to valve which are successively closed to the actuating fluid by the movement of theyalves from which they lead, means to exhaust the pressure from said closed passages, means to move said valves to close said passages, and means controlled by said valves to actuate motor-fluid valves.

16. In a governing mechanism for motors, a plurality of controller-valves, passages to serially conduct actuating fluid from valve to valve, means to lock part of said valves at one end of their stroke, while the valve or valves at the critical pointof regulation are free to move in either direction subject to variations in said actuating-pressure, and means controlled by said valves to actuate said motorfluid valves.

17 In a governingmechanism for motors,

a valve-casing, a plurality of chambers therein forming cylinders, passages leading from cylinder to cylinder and passages leading from said cylinders to an exhaust-pressure, means to-deliver to said cylinders a governed pressure, and piston-valves therein normally held by a constant pressure at one end of their stroke and successively actuated by said governed pressure, as its potential exceeds that of the constant pressure below the piston, to cut off the highand leave only an exhaust pressure opposing said governed pressure so that the piston is locked atthe other end of its stroke, and means controlled by said pistonvalves to actuate said motor-fluid valves.

18. In a governing mechanism for motors,

. a plurality of motor fluid valve controller means, means transmitting a governed power serlally from one to the other of said controller means, means to serlally transmit an opposing pressure from one to the other of said controller means and in a reverse direction to said governed power, means to look all but the valve or valves at the critical point of regulation in a definite position, and means controlled by said valves to operate motor-fluid valves.

19. In a governing mechanism for motors, a controller-casing provided with a plurality of fluid-actuated controller-valves and passages connecting said valves with a source of.

governed pressure in combination with a plurality of motor-fluid valves whose operation is governed by said controller means.

20. In a governing mechanism for motors,

a controller-casing comprising a series of fluidactuated valves and passages connecting said valves with a source of governed pressure and an exhaust-pressure in combination with a plurality of motor-fluid valves whose operation is governed by said controller means.

21. In a governing means for motors, a controller casing, a plurality of fluid actuated valves therein, and passages connecting said valves with a source of governed pressure, an

exhaust-pressure and a constant pressure incombination with a plurality of motor-fluid valves whose operation is governed by said controller means.

22. In a turbine, means to fractionally abstract the velocity of the motor-fluid a differ- A cut number of times in different working passages, in combination with a governor adjustable to accommodate its action to the different ratesof speed effected by said passages.

23. In a turbine, three nozzles and three sets i of rotating buckets, one set of buckets comber of times in one thanin the other of saidpassages. 1

25. In a turbine, two independent working passages designed to drive the turbine at different speeds of rotation by the interposition of a row or rows of stationary guides between rows of buckets in butone of said passages.

26. In a turbine, a plurality of concentric circular rows of working passages at different distances from the shaft center wherein the velocity of the motor-fluid pressure is frac-j tionally abstracted, and means to abstract the velocity a greater number of times in one row of passages than in the other or others.

27. In a turbine, two or more rows of fluidpressure nozzles, a rotating element having two or more rows of buckets in the line of the fluids flow from one of said rows of noz zles, stationary intermediates between said rows of buckets, and a single row of buckets opposite said other row of.nozzles.

28. In a turbine, means comprising nozzles, rotating buckets and stationary intermediates 5 to drive the turbine forward, to reverse it, and to operateit at a fraction of its forward driving speed, in combination with means; controlling the admission of motor fluid to said first-mentioned means, which operatewith only open and closed positions.

29. In a turbine a plurality of supply-nozzles, valves therefor having only open and closed positions, means to drive the turbine forward and to reverse it, and independent means to drive the turbine at a fraction of its full speed, in combination with means to cons trol the-operation of said valves.

30. In a turbine, three working passages which severally act to drive the turbine forward, to reverse it and to drive it at a fraction of its full speed, all of said passages acting to abstract substantially equal percentages of ve locity from said fluid.

31. In aturbine, means to drive the turbine forward at full speed, means to reverse the turbine, and means, independent of said for ward and reversing means, to drive the tur-' bine at a fraction of its full speed.

32. In a turbine, two independent working passages adapted to drive the turbine in the same direction and comprising means to fractionally abstract the velocity of the motor fluid a greater number of times in one than in the other of said passages, and means to drive the-turbine in a reverse direction to' that first mentioned. i

33. In combination, a two-speed and reversing turbine comprising independent rows of working passages, motor-fluid-controlling means and a governor adjustable to exert the same controlling efiect at each speed of rotation.

' 34. In a turbine, controller-valves actuated successively by a governor-power of varying potential, means controlled by said valves to deliver motor fluid to two or more rows of working passages, which drive said turbine at different speeds, a governor controlling said valve-actuating fluid and means to adjust the tension of said governor at different speeds.

35. In a turbine, a supply-head, a plurality of nozzle-passages leading therethrough, a motor-fluid-supply passage, and a plurality of branch passages leading substantially radially from said supply-passage which are closed at their outer ends and adapted to deliver motor fluid to one 'or more of said nozzles.

36. In a turbine, nozzle-passages, and rotary valves therefor, two or more of which are disposed in the same valve-seat end to end. 37. In aturbine, a plurality of rows of working passages, independent rows of rotary valves for said passages, and means to control the action of said valves.

38. Inaturbine, aplurality of rows of working passages at different distances from the shaft center, rows of fluid-actuated rotary valves for said passages, and means to control the action of said valves.

39. In a turbine, a plurality of rows of working passages at different distances from the shaft center, a circular valve-seat leading substantially radially across said rows and a plurality of rotary'valves insaid seat for said passages, and means to control the action of said valves. 1

L0. In a turbme, three concentric rows of nozzles and rotating buckets forming working passages, and governor-controlled fluid-actuating valves for SZJCl passages.

4L1. In a turbine, two or more working passages in which the fluid-pressure acts to drive a rotating element in reverse directions, supply and stage valves for said passages and governor controlled means to actuate said valves.

42. In a turbine, nozzles and rotating buckets forming independent working passages wherein'the' motor fluid acts with different speed-driving effects upon a rotating element of said turbine, and governor-controlled fiuid-' actuated valves in said passages;

43. In a motor, a plurality of turbine-valves, and a plurality of controller-valves each of which is adaptedto control a group of independent rows of turbine-supply and stage valves.

4A. In a motor, a plurality of groups of turbine-valves, independent actuating means connected to each valve of a group, and means to control said actuating means.

45. ,In a governing mechanism for motors, three concentric rows of working passages at different radial distances from the shaft center, and governing means controlling the admission of fluid-pressure to one of said rows at a time.

46. In a turbine operating by stage expansion two or more working passages at different distances from the shaft center, supply and stage valves for each passage and governing means to simultaneously admit an actuating fluid-pressure to the supply and stage valves of a passage.

I7. In a turbine acting by stage expansion, two or more rows of working passages comprising supply and stage nozzle passages, valves for said passages and a governing means for delivering fluid-pressure to the supply and stage valves of one of said rows at a time.

L8. In a turbine operating by stage expansion, two working passages at different distances from the shaft center and leading through all of the stages, and means in said passages to abstract the velocity of the motor fluid'a greater number of times in one than in the other.

49. In a turbine, a wheel-compartment and superheated means to receive the water of condensation and to retain it until evaporated.

50. In a turbine, a wheel-compartment, means to receive and hold the water of condensation until evaporated, and means to superheat said receiving means.

51. In a turbine, a rotating element and circumferential superheated projections disposed within said turbine and adapted to receive the water of condensation from said wheel and to retain it until it has evaporated.

52. In a turbine, a series of internal flanged projections forming receptacles in which the water of condensation collects, and means to superheat said projections to reevaporate said condensation.

53. In a turbine, a compartment within which a wheel rotates, circumferential ribs disposed around said compartment and provided with upturned edges to form circular receptacles for the water of condensation and a passage supplied with a heating agent and disposed to'superheat said ribs.

5&- In a turbine, three nozzle-passages at different distances from the shaft center, valves for said passages, fluid-pressure means to control the action of one of said valves, and means to maintain said other valves closed.

55. In a turbine, a plurality of concentric working passages, fluid-actuated valves for said passages, a controller means, separate passages conducting the valve-actuating fluid to said valves and arranged in groups leading each to one or more valves of each row of working passages and means to divert the governor controlled valve actuating fluid from said casing to one passage of each group.

56. In a turbine, rows ofworking passages and valves therefor at different distances from the shaft center, groups of passages conducting fluid-pressure to actuate a series of valves across said rows, means to control said valveactuating fluid and a multiported valve to direct said controlling fluid to the corresponding passage of each group.

' 57 In a motor, a controller-casing, motorfluid valves, groups of passages leading from said casing to said valves, a governor-controlled actuating fluid and a compound rotary valve admitting said fluid to a corresponding passage of each group and opening said other passages to a valve-closing pressure.

58. In a turbine having independent rows of working passages at different distances from the shaft center, rows of valves for said passages independently actuated by fluid-pressure, and a controlling means adapted to deliver a valveactuating pressure to one or more valves of one of said rows, and to expose said other rows to fluid-pressure means to maintain said latter rows of valves closed.

59. In a turbine, two independent working passages at different distances from the shaft center, said passages being substantially the same length and one of said passages provided With a greater number of rows of revolving buckets than said other passage, and stationary intermediates in said first-mentioned passage.

60. In a turbine operating by stage expansion, working passages and supply and stage valves therefor, a passage conducting valveactuating fluid to a row of valves across the stages and a fluid-actuated controller-valve admitting pressure to said passage.

61. In a motor, a plurality of motor-fluid valves a plurality of fluid-actuated controller means for said valves and a governing means for said valves, in combination with means to manually operate said controller means.

62. In a motor, a plurality of motor-fluid valves,a plurality of governor-controlled fluidactuated valves controlling the operation of said motor-fluid valves, and means to manually control the operation of said controllervalves.

68. In a two-speed motor, independent working passages to drive the motor at different speeds, means to pulsate the supply of motor fluid to one of said passages while the other is held closed.

64. In aturbine, a plurality of rows of supply-valves at difierent distances from the shaft center-,valves for said passages, and agoverning means for said valves adapted to confine its active control to one of said rows of valves and to pulsate one or more of the valves of said row, and means to close the other roW or rows of valves. 65. In a turbine, two independent supplypassages at difierent distances from the shaft center, and a controller means to pulsate the flow of fluid through one of said passages While the other passage is closed. v

66. In a turbine three independent supplypassages at different distances from the shaft center, and a controller means to pulsate the flow of fluid through one of, said passages While the other passages are closed,

67, In a turbine, supply-nozzle passages at different distances from the shaft center, valves 7 for said passages controlling the delivery of motor fluid against rotating buckets, and means to intermittently actuate one or more of the valves for passages equidistant from the shaft center While the passage or passages at different distances are closed.

68. In a fluid-pressure motor operatingby stage expansion, independent Working passages designed to exert diflerent driving effects on said motor and comprising supply and stage nozzles and valves and rotating buckets, and means to maintain one of said passages inactive and to interrupt the flow of motor fluid supplied to the active passage to deliver in the several compartments or stages.

In testimony whereof I have signed my name to this specification in the presence of tWo subscribing Witnesses.

' JAMES WILKINSON.

Witnesses: I

H. M. HARTON, R. D. JOHNSTON.

3O itin pulsations or blasts to the said buckets 

